CN105683620B - Dual clutch transmission - Google Patents
Dual clutch transmission Download PDFInfo
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- CN105683620B CN105683620B CN201480058517.4A CN201480058517A CN105683620B CN 105683620 B CN105683620 B CN 105683620B CN 201480058517 A CN201480058517 A CN 201480058517A CN 105683620 B CN105683620 B CN 105683620B
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/091—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears including a single countershaft
- F16H3/0915—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears including a single countershaft with coaxial input and output shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H3/097—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts the input and output shafts being aligned on the same axis
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H2003/0826—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts wherein at least one gear on the input shaft, or on a countershaft is used for two different forward gear ratios
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H2003/0933—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts with coaxial countershafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The present invention relates to a kind of dual clutch transmissions, prevent the deterioration of speed change sense.Has the 1st clutch (10),1st input shaft (11),2nd clutch (12),2nd input shaft (13),Output shaft (14),Countershaft (15),The 1st input gear including the 1st input master gear (20A) and the 1st input pinion (20B) is to (20),The 2nd input gear including the 2nd input master gear (21A) and the 2nd input pinion (21B) is to (21),The 1st change gear including the 1st output main gear (32A) and the 1st output pinion (32B) is to (32),The 2nd change gear including the 2nd output main gear (30A) and the 2nd output pinion (30B) is to (30),The 3rd change gear including the 3rd output main gear (31A) and the 3rd output pinion (31B) is to (31),1st input master gear (20A) or the 2nd output main gear (30A) are linked to the 1st link mechanism (40) of output shaft (14),2nd output pinion (30B) or the 3rd output pinion (31B) are linked to the 2nd link mechanism (41) of countershaft (15),And the 1st output main gear (32A) is linked to the 3rd link mechanism (42) of output shaft (14).
Description
Technical field
The present invention relates to a kind of dual clutch transmissions.
Background technology
In the past, it is known that a kind of dual clutch transmission has：1st input shaft is provided with the power from driving source
1st clutch of cut-out or engagement；2nd input shaft, be provided with by the 2nd of power cut or engagement from driving source the from
Clutch；And multiple speed change gear mesh, the dual clutch transmission by alternately switch the 1st clutch and the 2nd from
Clutch carries out speed change.
For example, a kind of dual clutch transmission is disclosed in patent document 1, by keeping off primary pinion to being used as 6
Speed change recycled with gear mesh, thus reduce speed change gear mesh.
Existing technical literature
Patent document
Patent document 1：Japanese Unexamined Patent Publication 2010-531417 bulletins
Invention content
The subject that the invention solves
It is above-mentioned to primary pinion to being recycled in the prior art, as shown in Figure 10 (A), 1 gear and 2 gear
Speed change, by the way that 1/2 gear dual-purpose change gear pair 320 is linked simultaneously the 1st primary pinion pair of optionally switch with input shaft 140
200 and the 2nd primary pinion pair 210 is realized.In addition, as shown in Figure 10 (B), the speed changes of 5 gears by by the 1st input shaft 110 with
Output shaft 140 directly links to realize, the speed changes of 6 gears are carried out again by regarding the 1st primary pinion pair 200 as speed change with gear mesh
Using realizing.
That is, in the dual clutch transmission of existing type, the stage gear ratio between 1~2 gear becomes the 1st primary pinion pair
The ratio between the gear ratio of 200 gear ratio and the 2nd primary pinion pair 210,5~6 gear between stage gear ratio become the 2nd primary pinion pair
The product of inverse of the gear ratio of 210 gear ratio and the 1st primary pinion pair 200, the grade biography between 1~2 gear and between 5~6 gears
Dynamic ratio becomes to be equal to each other.
Continuous sense (hereinafter referred to as speed change sense) when under normal circumstances, in order to ensure speed change, preferably slow speed turbine stage is then
More expand stage gear ratio, and high speed grade then gets over constriction stage gear ratio.But in above-mentioned dual clutch transmission, by
Stage gear ratio between 1~2 gear and between 5~6 gears is equal to each other, therefore they can not be individually set as to best value,
And there is the project for making speed change sense deteriorate.
The purpose of the dual clutch transmission of the present invention is, is effectively prevented the deterioration of speed change sense.
Means for solving the problems
The dual clutch transmission of the present invention has：1st input shaft, have the power cut from driving source or
1st clutch of engagement；2nd input shaft has the 2nd clutch of power cut or engagement from above-mentioned driving source；
Output shaft, on the same axis with the configuration of above-mentioned 1st input shaft；Countershaft, with above-mentioned 1st input shaft, above-mentioned 2nd input shaft and above-mentioned
Output shaft parallelly configures；1st input gear mesh, including be fixed on above-mentioned 1st input shaft the 1st input master gear and
The 1st input pinion that above-mentioned countershaft can be set to the relative rotation and engaged with above-mentioned 1st input master gear；2nd input
With gear mesh, including be fixed on the 2nd input master gear of above-mentioned 2nd input shaft and be fixed on above-mentioned countershaft and with the above-mentioned 2nd
Input the 2nd input pinion of master gear engagement；1st speed change gear mesh, including can be set to the relative rotation above-mentioned defeated
1st output main gear of shaft and it is fixed on above-mentioned countershaft and the 1st secondary tooth of output that is engaged with above-mentioned 1st output main gear
Wheel；2nd speed change gear mesh, including can be set to the relative rotation than above-mentioned 1st output main gear by the upper of input end side
State the 2nd output main gear of output shaft and be formed to rotate integrally with above-mentioned 1st input pinion and with the above-mentioned 2nd
2nd output pinion of output main gear engagement；3rd speed change gear mesh, including be fixed on above-mentioned 2nd output main gear with it is upper
It states the 3rd output main gear of the above-mentioned output shaft between the 1st output main gear and above-mentioned pair can be set to the relative rotation
Axis and engaged with above-mentioned 3rd output main gear the 3rd output pinion；1st connection unit can input main tooth by the above-mentioned 1st
Wheel and above-mentioned 2nd output main gear are selectively connected in above-mentioned output shaft；2nd connection unit can be exported the above-mentioned 2nd
Pinion and above-mentioned 3rd output pinion are selectively connected in above-mentioned countershaft；And the 3rd connection unit, it at least can will
Above-mentioned 1st output main gear is selectively connected in above-mentioned output shaft.
The effect of invention
Dual clutch transmission according to the present invention can be effectively prevented the deterioration of speed change sense.
Description of the drawings
Fig. 1 is the synoptic diagram for the dual clutch transmission for indicating an embodiment of the invention.
Fig. 2 is the figure of the power transfer path for 1 gear for indicating dual clutch transmission shown in FIG. 1.
Fig. 3 is the figure of the power transfer path for 2 gears for indicating dual clutch transmission shown in FIG. 1.
Fig. 4 is the figure of the power transfer path for 3 gears for indicating dual clutch transmission shown in FIG. 1.
Fig. 5 is the figure of the power transfer path for 4 gears for indicating dual clutch transmission shown in FIG. 1.
Fig. 6 is the figure of the power transfer path for 5 gears for indicating dual clutch transmission shown in FIG. 1.
Fig. 7 is the figure of the power transfer path for 6 gears for indicating dual clutch transmission shown in FIG. 1.
Fig. 8 is the figure of the power transfer path for 7 gears for indicating dual clutch transmission shown in FIG. 1.
Fig. 9 is the chart illustrated to an example of the stage gear ratio of present embodiment.
Figure 10 is the figure illustrated to the power transfer path of the dual clutch transmission of existing type.
Specific implementation mode
Hereinafter, being illustrated to the dual clutch transmission of an embodiment of the invention based on attached drawing.To identical
Component mark identical symbol, the title and function of these components are also identical.Thus, it does not repeat to carry out these components detailed
It describes in detail bright.
As shown in Figure 1, being provided with the 1st clutch 10 in the input side of the 1st input shaft 11.In the defeated of the 2nd input shaft 13
Entry end is provided with the 2nd clutch 12.It is formed with the hollow shaft penetrated through in an axial direction in the 2nd input shaft 13, and in the hollow shaft
In can insert the 1st input shaft with the relative rotation.
Output shaft 14 and the 1st input shaft 11 configure on the same axis at spaced intervals.Jackshaft 15 and input shaft 11,13 and
Output shaft 14 parallelly configures.
1st clutch 10 has：It is fixed on the 1st pressing plate 10A of the bent axle 3 of engine 2；And it is fixed on the 1st input shaft
1st clutch disc 10B of 11 input side.When being crimped on the 1st clutch disc 10B when the 1st pressing plate 10A is mobile, engine 2
Power be transferred to the 1st input shaft 11 via the 1st clutch 10.
2nd clutch 12 has：It is fixed on the 2nd pressing plate 12A of the bent axle 3 of engine 2；And it is fixed on the 2nd input shaft
2nd clutch disc 12B of 13 input side.When being crimped on the 2nd clutch disc 12B when the 2nd pressing plate 12A is mobile, engine 2
Power be transferred to the 2nd input shaft 13 via the 2nd clutch 12.
1st primary pinion pair 20 is an example of the 1st input gear mesh of the present invention, has the 1st input being engaged with each other
Gear 20A and the 1st counter gear 20B.1st input gear 20A is fixed on the delivery side of the 1st input shaft 11.1st reversion tooth
Wheel 20B can be set to jackshaft 15 with the relative rotation, and be formed as one with aftermentioned 3 gear counter gear 30B.
2nd primary pinion pair 21 is an example of the 2nd input gear mesh of the present invention, has the 2nd input being engaged with each other
Gear 21A and the 2nd counter gear 21B.2nd input gear 21A is fixed on the delivery side of the 2nd input shaft 13.2nd reversion tooth
Wheel 21B is fixed on the input side of jackshaft 15.That is, the engine 2 of the 2nd input shaft 13 is transferred to via the 2nd clutch 12
Power is transferred directly to jackshaft 15 via the 2nd primary pinion pair 21.
3 gear change gears pair 30 are an examples of the 2nd speed change gear mesh of the present invention, and it is defeated to have 3 gears being engaged with each other
Go out the gear counter gears of gear 30A and 3 30B.3 gear output gear 30A can be set to output shaft 14 with the relative rotation.3 gears are anti-
Rotating disk 30B is formed to rotate integrally with the 1st counter gear 20B.In more detail, in the 1st integrally formed reversion tooth
The gears of wheel 20B and 3 counter gear 30B is formed with the hollow shaft penetrated through in an axial direction, and is rotatably freely inserted in the hollow shaft
It is connected with jackshaft 15.The number of teeth of 3 gear output gear 30A is set to the number of teeth more than 3 gear counter gear 30B.
6 gear change gears pair 31 are an examples of the 3rd speed change gear mesh of the present invention, and it is defeated to have 6 gears being engaged with each other
Go out the gear counter gears of gear 31A and 6 31B.6 gear output gear 31A are fixed on the gear counter gear of output shaft 14,6 31B being capable of phase
To being rotatably provided in jackshaft 15.The number of teeth of 6 gear output gear 31A is set to the number of teeth less than 6 gear counter gear 31B.
1/2 gear dual-purpose change gear pair 32 is an example of the 1st speed change gear mesh of the present invention, has 1/ to be engaged with each other
2 gear output gear 32A and 1/2 gear counter gear 32B.1/2 gear output gear 32A can be set to output shaft with the relative rotation
14,1/2 gear counter gear 32B are fixed on jackshaft 15.The number of teeth of 1/2 gear output gear 32A is set to invert more than 1/2 gear
The number of teeth of gear 32B.
Reverse gear have with change gear pair 33 the reverse output gear 33A being engaged with each other and reverse gear counter gear 33B and
Idler gear 33C.Reverse output gear 33A can be set to output shaft 14 with the relative rotation, and the counter gear 33B that reverses gear is fixed on
Jackshaft 15.
4 gear change gears pair 34 are an examples of the 4th speed change gear mesh of the present invention, and it is defeated to have 4 gears being engaged with each other
Go out the gear counter gears of gear 34A and 4 34B.It is anti-that 4 gear output gear 34A can be set to the gear of output shaft 14,4 with the relative rotation
Rotating disk 34B is fixed on jackshaft 15.The number of teeth of 4 gear output gear 34A is set to the number of teeth more than 4 gear counter gear 34B.
1st lazy-tongs 40 are an examples of the 1st connection unit of the present invention, are had：1st sleeve 40A, can with it is not shown
The gear shift operation of shift lever device be correspondingly axially moveable；Spline 40B is fixed on the input side of output shaft 14；Spline
40C is fixed on the 1st input gear 20A；And spline 40D, it is fixed on 3 gear output gear 30A.
When engage with spline 40C when the 1st sleeve 40A is mobile towards the 1st sides input gear 20A, the 1st input gear 20A and
The connection of output shaft 14 (the 1st input shaft 11 directly links with output shaft 14).On the other hand, when the 1st sleeve 40A keeps off output gears towards 3
When taking turns the movement of the sides 30A and engaging with spline 40D, 3 gear output gear 30A link with output shaft 14.That is, be configured to, it is same by the 1st
Step mechanism 40 can be such that the gears of the 1st input gear 20A and 3 output gear 30A is selectively connected to output shaft 14.
2nd lazy-tongs 41 are an examples of the 2nd connection unit of the present invention, are had：2nd sleeve 41A can be moved in an axial direction
It is dynamic；Spline 41B, the jackshaft 15 being fixed between the gear counter gears of 3 gear counter gear 30B and 6 31B；Spline 41C, is fixed on 3
Keep off counter gear 30B；And spline 41D, it is fixed on 6 gear counter gear 31B.
When the 2nd sleeve 41A it is mobile towards 3 gear counter gear 30B sides and when engage with spline 41C, 3 gear counter gear 30B and
Jackshaft 15 links.On the other hand, when the 2nd sleeve 41A keeps off the movement of the sides counter gear 31B towards 6 and engages with spline 42D, 6 gears
Counter gear 31B links with jackshaft 15.That is, be configured to, by the 2nd lazy-tongs 41 can make 3 gear counter gear 30B and
6 gear counter gear 31B are selectively connected to jackshaft 15.
3rd lazy-tongs 42 are an examples of the 3rd connection unit of the present invention, are had：3rd sleeve 42A can be moved in an axial direction
It is dynamic；Spline 42B, the output shaft 14 being fixed between 1/2 gear output gear 32A and reverse output gear 33A；Spline 42C, it is fixed
In 1/2 gear output gear 32A；And spline 42D, it is fixed on reverse output gear 33A.
When engaging with spline 42C when the 3rd sleeve 42A is mobile towards 1/2 sides gear output gear 32A, 1/2 gear output gear
32A links with output shaft 14.On the other hand, when the 3rd sleeve 42A engages towards the movement of the sides reverse output gear 33A with spline 42D
When, reverse output gear 33A links with output shaft 14.That is, being configured to, 1/2 gear output gear can be made by the 3rd lazy-tongs 42
Wheel 32A and reverse output gear 33A is selectively connected to output shaft 14.
4th lazy-tongs 43 are an examples of the 4th connection unit of the present invention, are had：4th sleeve 43A can be moved in an axial direction
It is dynamic；Spline 43B is fixed on the output shaft 14 that output end is leaned on than 4 gear output gear 34A；And spline 43C, it is defeated to be fixed on 4 gears
Go out gear 34A.
When the 4th sleeve 43A it is mobile towards 4 gear output gear 34A sides and when engage with spline 43C, 4 gear output gear 34A and
Output shaft 14 links.That is, being configured to, 4 gear output gear 34A and 14 selectivity of output shaft can be made by the 4th lazy-tongs 43
Ground links.
The gear shift operation of transmission control unit (TCU) 80 and gearshift (not shown), which correspondingly executes, makes the 1st clutch
The speed Control that device 10, the 2nd clutch 12, each lazy-tongs 40~43 work.Hereinafter, the speed change based on Fig. 2~8 pair TCU80
The power transfer path of each DR Drive Range of control illustrates.
Fig. 2 indicates the power transfer path of 1 gear.In the case where 1 keeps off, the 1st clutch 10 is selected, the 2nd synchronous machine is passed through
Structure 41 links 3 gear counter gear 30B with jackshaft 15, by 1/2 gear output gear 32A and is exported by the 3rd lazy-tongs 42
Axis 14 links.
That is, the power of engine 2 is inverted from the 1st clutch 10 via the 1st input shaft 11, the 1st primary pinion pair 20,3 gear
Gear 30B, jackshaft 15,1/2 keep off dual-purpose change gear pair 32 and are transferred to output shaft 14.
Fig. 3 indicates the power transfer path of 2 gears.In the case where 2 keep off, by from the state of 1 gear by the 1st clutch 10
The 2nd clutch 12 is switched to execute.That is, the power of engine 2 is primary via the 2nd input shaft the 13, the 2nd from the 2nd clutch 12
Gear mesh 21, jackshaft 15,1/2 keep off dual-purpose change gear pair 32 and are transferred to output shaft 14.
Fig. 4 indicates the power transfer path of 3 gears.In the case where 3 keep off, execute as follows：By the in the state that 2 keep off
1 lazy-tongs 40 link 3 gear output gear 30A and output shafts 14 for standby mode, and the 2nd clutch 12 is switched to the
1 clutch 10.
That is, the power of engine 2 becomes from the 1st clutch 10 via the 1st input shaft 11, the 1st primary pinion pair 20,3 gears
Fast gear mesh 30 is transferred to output shaft 14.
Fig. 5 indicates the power transfer path of 4 gears.In the case where 4 keep off, execute as follows：By the in the state that 3 keep off
4 lazy-tongs 43 link 4 gear output gear 34A and output shafts 14 for standby mode, and the 1st clutch 10 is switched to the
2 clutches 12.
That is, the power of engine 2 from the 2nd clutch 12 via the 2nd input shaft 13, the 2nd primary pinion pair 21, jackshaft
15,4 gear change gears pair 34 are transferred to output shaft 14.
Fig. 6 indicates the power transfer path of 5 gears.In the case where 5 keep off, execute as follows：By the in the state that 4 keep off
1st input gear 20A and the connection of output shaft 14 (directly linking) are become standby mode by 1 lazy-tongs 40, by the 2nd clutch
12 switch to the 1st clutch 10.
That is, the power of engine 2 is transferred to output from the 1st clutch 10 via the 1st input shaft 11, the 1st input gear 20A
Axis 14.
Fig. 7 indicates the power transfer path of 6 gears.In the case where 6 keep off, execute as follows：By the in the state that 5 keep off
2 lazy-tongs 41 link 6 gear counter gear 31B and jackshafts 15 for standby mode, and the 1st clutch 10 is switched to the
2 clutches 12.
That is, the power of engine 2 from the 2nd clutch 12 via the 2nd input shaft 13, the 2nd primary pinion pair 21, jackshaft
15,6 gear change gears pair 31 are transferred to output shaft 14.
Fig. 8 shows the power transfer paths of 7 gears.In the case where 7 keep off, the 2nd clutch 12 is made in the state that 6 keep off temporarily
Cut-out.Then, it executes as follows：The 1st input gear 20A is linked with output shaft 14 by the 1st lazy-tongs 40, passes through the 2nd
Lazy-tongs 41 link 3 gear counter gear 30B with jackshaft 15, and again connect the 2nd clutch 12.
That is, the power of engine 10 from the 2nd clutch 12 via the 2nd input shaft 13, the 2nd primary pinion pair 21, jackshaft
15,3 gear counter gear 30B, the 1st primary pinion pair 20 are transferred to output shaft 14.Hereby it is achieved that 20 conduct of the 1st primary pinion pair
The recycling of speed change gear mesh.In addition, making the 2nd clutch 12 cut off or engage in the shift of 6~7 gears, therefore can produce
Raw so-called loss of machine of torque, but due to being high speed grade, influence smaller.
Then, the gear ratio and stage gear ratio of the dual clutch transmission of present embodiment are illustrated.In addition,
Each numerical value used in the following description is an example of present embodiment, can be fitted without departing from the spirit and scope of the invention
When being set to best value.
Table 1 below indicates that the number of teeth of each gear mesh and an example of gear ratio, table 2 below indicate each shift gear 1~7
Gear ratio.In addition, in table 1, the tooth number Z 1 on upper layer indicates the number of teeth for being set to the gear of jackshaft 15, the tooth number Z 2 in middle level
Indicate the number of teeth for being set to the gear of input shaft 11,13 or output shaft 14.
[table 1]
| Pri-1 | Pri-2 | 3rd | 6th | 1st/2nd | 4th | |
| Tooth number Z 1 | 28 | 40 | 30 | 37 | 13 | 27 |
| Tooth number Z 1 | 45 | 39 | 39 | 29 | 43 | 39 |
| Gear ratio | 1.61 | 0.98 | 1.30 | 0.78 | 3.31 | 1.44 |
[table 2]
| 1st | 2nd | 3rd | 4th | 5th | 6th | 7th | |
| Primary pinion ratio | 1.61 | 0.98 | 1.61 | 0.98 | 1.00 | 0.98 | 0.98 |
| Change gear ratio | 3.31 | 3.31 | 1.30 | 1.44 | 1.00 | 0.78 | 0.62 |
| Resultant gear retio | 5.316 | 3.225 | 2.089 | 1.408 | 1.000 | 0.764 | 0.607 |
When sought according to table 2 1~2 gear between and 5~7 gear between each stage gear ratio when, 1~2 gear between stage gear ratio at
It is about 1.648 (/ 2 gears of=1 gear), the stage gear ratio of 5~7 gears also becomes about 1.648 (/ 7 gears of=5 gear), they are big each other
It causes equal.In order to be well maintained speed change sense, the preferably widely stage gear ratio of setting slow speed turbine stage side, and narrowly setting high-speed
The stage gear ratio of grade side.In the present embodiment, 6 gear change gears pair 31 are provided with, which is i.e.
Just expand the stage gear ratio between 1~2 gear and concomitantly expand the stage gear ratio between 5~7 gears, it also can be independently
Gear ratio is set, therefore for example shown in Figure 10, is capable of the stage gear ratio of narrowly setting high-speed grade side.
In addition, 3 gear change gears pair 30, the 1/2 gear dual-purpose change gear pair 32 and 4 as reduction gearing pair is kept off
It is all dallied with the output gear of change gear pair 34 and is supported on output shaft 14, only as 6 gear gear teeth of speed increasing gear pair
It takes turns and output shaft 14 is fixed on to 31 output gear 31A.Thus, there is no relative to output shaft 14 always by the reversion tooth of speedup
Wheel can effectively inhibit and generate heat, wears caused by high speed rotation etc..
Then, the function and effect of the dual clutch transmission of present embodiment are illustrated.
In the dual clutch transmission of existing type, 1~2 gear between stage gear ratio and 5~6 gear between stage gear ratio that
This is equal, therefore they can not be individually set as to best value, there is the project for the deterioration for leading to speed change sense.
In contrast, in the dual clutch transmission of present embodiment, although 1~2 gear between stage gear ratio and 5~
Stage gear ratio between 7 gears is equal to each other, but the 6 gear gear teeth that can independently set gear ratio are provided between 5~7 gears
Wheel is to 31.That is, be configured to, even if in order to keep speed change sense good and make the 1~2 of low speed side stage gear ratio expansion keep off and and this
Concomitantly expand the stage gear ratio between 5~7 gears, can also pass through the 6 gear change gears pair that are made up being kept off between 5~7
31 the stage gear ratio of high speed grade side is set to it is relatively narrow.Thus, dual clutch transmission according to the present embodiment, Neng Goushe
Fixed high speed grade side then becomes narrower good stage gear ratio, can effectively improve speed change sense.
In addition, in the dual clutch transmission of existing type, reduction gearing is to (for example, 4 gear change gears to)
Output gear is fixed in output shaft.Therefore, when output shaft high speed rotation, counter gear is further increased compared with output shaft
Speed and rotate, exist cause fever, abrasion, loss increase etc. project.
In contrast, in the dual clutch transmission of present embodiment, only 6 gear output gear 31A are fixed on output
Axis 14, the idle running of other output gears are supported on output shaft 14.6 gear change gears pair 31 are speed increasing gear pair, therefore output shaft
14 rotation is decelerated and is transferred to 6 gear counter gear 31B always.Thus, double-clutch type speed change according to the present embodiment
Device, there is no relative to output shaft 14 always by the counter gear of speedup, therefore can effectively inhibit counter gear fever,
Abrasion, loss increase etc..
In addition, the present invention is not limited to the above embodiment, can fit without departing from the spirit and scope of the invention
When shifting ground is implemented.
For example, 3 gear counter gear 30B and the 1st counter gear 20B can also divide it is not absolutely required to be integrally formed
Formed to body.In this case, as long as being configured to that 3 gear counter gear 30B and the 1st are inverted tooth by lazy-tongs etc.
Wheel 20B is selectively connected to jackshaft 15.
The explanation of symbol
2：Engine；10：1st clutch；11：1st input shaft；12：2nd clutch；13：2nd input shaft；14：Output
Axis；15：Jackshaft；20：1st primary pinion pair；21：2nd primary pinion pair；30：3 gear change gears pair；31：6 gears become
Fast gear mesh；32：1/2 gear dual-purpose change gear pair；34：4 gear change gears pair；40：1st lazy-tongs；41：2nd synchronizes
Mechanism；42：3rd lazy-tongs；43：4th lazy-tongs.
Claims (3)
1. a kind of dual clutch transmission, has：
1st input shaft has the 1st clutch of power cut or engagement from driving source；
2nd input shaft has the 2nd clutch of power cut or engagement from above-mentioned driving source；
Output shaft, on the same axis with the configuration of above-mentioned 1st input shaft；
Countershaft is parallelly configured with above-mentioned 1st input shaft, above-mentioned 2nd input shaft and above-mentioned output shaft；
1st input gear mesh, including it is fixed on the 1st input master gear and can be with the relative rotation of above-mentioned 1st input shaft
The 1st input pinion for being set to above-mentioned countershaft and being engaged with above-mentioned 1st input master gear；
2nd input gear mesh, including be fixed on the 2nd input master gear of above-mentioned 2nd input shaft and be fixed on above-mentioned countershaft
And the 2nd input pinion engaged with above-mentioned 2nd input master gear；
1st speed change gear mesh, including it can be set to the 1st output main gear, the Yi Jigu of above-mentioned output shaft with the relative rotation
Due to the 1st output pinion that above-mentioned countershaft is engaged with above-mentioned 1st output main gear；
2nd speed change gear mesh, including can be set to the relative rotation than above-mentioned 1st output main gear by the upper of input end side
State the 2nd output main gear of output shaft and be formed to rotate integrally with above-mentioned 1st input pinion and with the above-mentioned 2nd
2nd output pinion of output main gear engagement；
3rd speed change gear mesh, including be fixed on above-mentioned between above-mentioned 2nd output main gear and above-mentioned 1st output main gear
3rd output main gear of output shaft and it can be set to above-mentioned countershaft with the relative rotation and be nibbled with above-mentioned 3rd output main gear
The 3rd output pinion closed；
4th speed change gear mesh, including can be set to the relative rotation than above-mentioned 1st output main gear by the upper of output end
The 4th for stating the 4th output main gear of output shaft and being fixed on above-mentioned countershaft and being engaged with above-mentioned 4th output main gear exports
Pinion；
1st connection unit can input master gear by the above-mentioned 1st and above-mentioned 2nd output main gear is selectively connected in upper
State output shaft；
2nd connection unit can export pinion by the above-mentioned 2nd and above-mentioned 3rd output pinion is selectively connected in upper
State countershaft；
Above-mentioned 1st output main gear can be at least selectively connected in above-mentioned output shaft by the 3rd connection unit；And
Above-mentioned 4th output main gear can be at least selectively connected in above-mentioned output shaft by the 4th connection unit,
The above-mentioned 3rd is being exported after pinion links with above-mentioned countershaft from above-mentioned 1st clutch by above-mentioned 2nd connection unit
It is switched to above-mentioned 2nd clutch, thus inputs master gear and above-mentioned output shaft by the above-mentioned 1st from by above-mentioned 1st connection unit
The traveling grade of connection is to high speed grade speed change, later, by above-mentioned 2nd clutch cut off after by above-mentioned 1st connection unit into
The connection of the above-mentioned 1st input master gear of row and above-mentioned output shaft, and it is defeated by above-mentioned 2nd connection unit progress the above-mentioned 2nd
Go out the connection of pinion and above-mentioned countershaft, and again connect above-mentioned 2nd clutch, thus to higher speed grade speed change.
2. dual clutch transmission as described in claim 1, wherein
Above-mentioned 1st speed change gear mesh, above-mentioned 2nd speed change gear mesh and above-mentioned 4th speed change are by output shaft with gear mesh
The number of gear teeth of side is set to the deceleration gear mesh of the number of gear teeth more than countershaft side,
Above-mentioned 3rd speed change is the speedup that the number of gear teeth of output shaft side is set to the number of gear teeth less than countershaft side with gear mesh
Use gear mesh.
3. dual clutch transmission as claimed in claim 1 or 2, wherein
The above-mentioned 1st speed change change gear pair that gear mesh is 1 gear and 2 gear dual-purposes,
Above-mentioned 3rd speed change is the change gear pair of 6 gears with gear mesh,
In the case where 7 keep off, above-mentioned 2nd clutch is made to engage, pinion is exported by the above-mentioned 2nd by above-mentioned 2nd connection unit
Link with above-mentioned countershaft, and master gear is inputted by the above-mentioned 1st by above-mentioned 1st connection unit and is linked with above-mentioned output shaft, it will be upper
It states the 1st input and is utilized as speed change gear mesh with gear mesh.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013225221A JP6295604B2 (en) | 2013-10-30 | 2013-10-30 | Twin clutch transmission |
| JP2013-225221 | 2013-10-30 | ||
| PCT/JP2014/077695 WO2015064389A1 (en) | 2013-10-30 | 2014-10-17 | Dual-clutch transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105683620A CN105683620A (en) | 2016-06-15 |
| CN105683620B true CN105683620B (en) | 2018-08-21 |
Family
ID=53003998
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480058517.4A Expired - Fee Related CN105683620B (en) | 2013-10-30 | 2014-10-17 | Dual clutch transmission |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20160238109A1 (en) |
| EP (1) | EP3064803B1 (en) |
| JP (1) | JP6295604B2 (en) |
| CN (1) | CN105683620B (en) |
| WO (1) | WO2015064389A1 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6772742B2 (en) * | 2016-10-07 | 2020-10-21 | いすゞ自動車株式会社 | Dual clutch transmission |
| JP6729319B2 (en) * | 2016-11-18 | 2020-07-22 | いすゞ自動車株式会社 | Dual clutch transmission |
| DE102017204336A1 (en) | 2017-03-15 | 2018-09-20 | Wirtgen Gmbh | Soil cultivation machine with manual transmission between drive motor and rotatable working device |
| CN107489740B (en) * | 2017-09-04 | 2019-06-18 | 北京理工大学 | Longitudinal seven speed dual clutch gearbox |
| CN112193048B (en) * | 2020-10-23 | 2022-05-24 | 东风汽车集团有限公司 | Multi-mode driving system of hybrid power vehicle |
| DE102023200195A1 (en) | 2023-01-12 | 2024-07-18 | Zf Friedrichshafen Ag | Powershift transmission for a group-design motor vehicle transmission, motor vehicle transmission and agricultural or municipal utility vehicle |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101501365A (en) * | 2006-08-08 | 2009-08-05 | 五十铃自动车株式会社 | Output shaft speed reduction-type dual clutch transmission |
| CN101688588A (en) * | 2007-06-26 | 2010-03-31 | 戴姆勒股份公司 | Toothed-wheel variable-speed transmission |
| CN103256344A (en) * | 2012-02-21 | 2013-08-21 | Zf腓德烈斯哈芬股份公司 | Transmission for a motor-vehicle |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61274147A (en) * | 1985-05-28 | 1986-12-04 | Mazda Motor Corp | Gear type speed changer |
| DE102004043387B4 (en) * | 2004-09-08 | 2015-05-28 | Zf Friedrichshafen Ag | Multi-speed gearbox in countershaft design |
| DE102004043386B4 (en) * | 2004-09-08 | 2013-02-21 | Zf Friedrichshafen Ag | Transmission device in countershaft design |
-
2013
- 2013-10-30 JP JP2013225221A patent/JP6295604B2/en not_active Expired - Fee Related
-
2014
- 2014-10-17 US US15/030,172 patent/US20160238109A1/en not_active Abandoned
- 2014-10-17 EP EP14857848.7A patent/EP3064803B1/en active Active
- 2014-10-17 CN CN201480058517.4A patent/CN105683620B/en not_active Expired - Fee Related
- 2014-10-17 WO PCT/JP2014/077695 patent/WO2015064389A1/en active Application Filing
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101501365A (en) * | 2006-08-08 | 2009-08-05 | 五十铃自动车株式会社 | Output shaft speed reduction-type dual clutch transmission |
| CN101688588A (en) * | 2007-06-26 | 2010-03-31 | 戴姆勒股份公司 | Toothed-wheel variable-speed transmission |
| CN103256344A (en) * | 2012-02-21 | 2013-08-21 | Zf腓德烈斯哈芬股份公司 | Transmission for a motor-vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| US20160238109A1 (en) | 2016-08-18 |
| JP6295604B2 (en) | 2018-03-20 |
| JP2015086930A (en) | 2015-05-07 |
| WO2015064389A1 (en) | 2015-05-07 |
| EP3064803A4 (en) | 2017-12-06 |
| EP3064803B1 (en) | 2020-08-19 |
| CN105683620A (en) | 2016-06-15 |
| EP3064803A1 (en) | 2016-09-07 |
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